Control of an active suspension system for a work vehicle based upon a parameter of another vehicle system

ABSTRACT

An active suspension system for a work vehicle is disclosed herein. The system includes at least one active vibration isolator mounted between the chassis and cab of the vehicle. The isolator moves the cab relative to the chassis in response to a control signal generated by a control circuit. The control circuit communicates to a second vehicle system via a communication interface. The communicated data includes a parameter of the second vehicle system related to a force applied to the vehicle during operation of the second vehicle system. The control signal is generated at least partly in response to the parameter so as to minimize the vibration on the cab caused by operation of the second vehicle system. Cab movement may be disabled when ground speed of the vehicle is below a predetermined speed threshold or when an operator presence sensor detects that the operator is not present.

FIELD OF THE INVENTION

The present invention relates generally to the field of activesuspension systems. More particularly, the invention relates to anactive suspension system for a work vehicle which includes at least oneactive vibration isolator, wherein a control circuit communicatesbetween the isolator and another vehicle system and generates controlsignals for the isolator which depend at least partly upon a parameterof the another vehicle system.

BACKGROUND OF THE INVENTION

The ride quality and operator comfort of a work vehicle is adverselyaffected by vibrations or movement transmitted from the frame or chassisof the vehicle to the operator's cab. As the work vehicle travels acrossa surface, movement of the chassis induces the operator's cab to pitch,roll and bounce. Movement of the cab can be particularly severe inagricultural and construction equipment vehicles (e.g., tractors,combines, backhoes, cranes, dozers, trenchers, skid-steer loaders, etc.)because such vehicles typically operate on off-road surfaces or fieldshaving a high level of bumpiness.

Operator comfort may also be adversely affected by the operation ofvarious systems on a work vehicle. In particular, operation of variouswork vehicle systems can cause forces to be applied to the chassis ofthe vehicle which, in turn, are transmitted to the cab. Examples ofthese forces include the following: draft forces exerted on the hitch ofan agricultural tractor by an implement (e.g., a plow) which can causethe cab to pitch; normal forces applied to a work vehicle as the vehicleturns in response to a steering device which can cause the cab to roll;clutch forces generated when a work vehicle clutch (e.g., a main driveclutch; four-wheel drive clutch) is engaged or disengaged which cancause the cab to pitch; gear shift forces generated when a transmissionof a work vehicle is shifted which can cause the cab to pitch; brakingforces generated as brakes of a work vehicle are operated which cancause the cab to pitch; acceleration forces generated when a speedactuator changes the speed of a work vehicle which can cause the cab topitch; etc.

The movement of the cab caused by surface bumps and the operation ofvehicle systems cause both qualitative and quantitative problems. Anoperator of such a vehicle experiences increased levels of discomfortand fatigue caused by the vibrations. Productivity is decreased when anoperator is forced to rest or shorten the work day, or is unable toefficiently control the work vehicle. The operator is also less likelyto be satisfied with a work vehicle which provides poor ride quality.Under certain conditions, the frequency and magnitude of cab movementmay force the operator to decrease driving speed, further decreasingproductivity.

To improve ride quality and operator comfort, work vehicles have beenequipped with passive, semi-active or active suspension systems toisolate the operator from vibrations caused by surface bumps. Suchsystems include vibration isolators mounted between the chassis and cabor seat. Passive systems use passive vibration isolators (e.g., rubberisolators, springs with friction or viscous dampers) to damp vibrationswith different isolators used to damp different frequencies. Rubberisolators may be used, for example, to damp high frequency vibrationsand air bags used to damp low frequency vibrations. However, performanceof passive systems is limited due to design compromises needed toachieve good control at resonance frequencies and good isolation at highfrequencies.

Semi-active systems achieve control and isolation between the chassisand the cab by controlling a damper to selectively remove energy fromthe system in response to movement of the cab sensed by sensors. Activesystems use sensors to sense cab movement and a controller to generatecontrol signals for an actuator which applies a force to the cab tocancel vibrations transmitted to the cab by the chassis. The powerneeded to apply the force is supplied by an external source (e.g.,hydraulic pump).

As the above paragraphs imply, it is desirable that a suspension systemattenuate both low and high frequency vibrations between the chassis andcab. Attenuation of high frequency vibrations can decrease acousticnoise in the cab, decrease fatigue and decrease vibration-inducedmechanical faults. Attenuation of low frequency (e.g., less than 20 Hz)vibrations can decrease operator fatigue and improve vehicleoperability. The attenuation of low frequency vibrations is particularlyimportant because the resonant frequencies of the human body aretypically below 20 Hz. For example, the human abdomen resonates atfrequencies between 4-8 Hz, the head and eyes resonate at frequenciesaround 10 Hz, and the torso at 1-2 Hz. The actual frequency may varywith the particular individual.

One active suspension system for a work vehicle includes a hydraulicactuator mounted at a single point between the rear of the cab and thevehicle frame. The front of the cab is pivotally mounted to the frame.The actuator is controlled to move the cab relative to the frame inresponse to sensed acceleration signals. The system includes a singleair bag used to level the cab. This system, however, only affects cabpitch since the actuator can only pivot the cab about the single point.Further, the control signals applied to the actuator do not depend onparameters of other vehicle systems which are indicative of forcesapplied to the vehicle due to operation of those systems. Thus, thesystem does not specifically react to the forces caused by othersystems.

Another active suspension system for a work vehicle includes one activevibration isolator mounted between the vehicle chassis and the rear ofthe cab, and two active isolators mounted between the chassis and thefront of the cab. Each isolator includes a hydraulic actuator mountedbetween the chassis and the cab, and an air bag to support the weight ofthe cab. The actuator is controlled to move the cab relative to thechassis in response to sensed acceleration signals. Each isolator isindividually controlled by an electronic controller replicated for eachisolator. Thus, the control signals applied to the actuators are notcoordinated with each other to provide coordinated control of theisolators. Further, as with the other system, the control signalsapplied to the actuator do not depend on parameters of other vehiclesystems indicative of forces applied to the vehicle due to operation ofthose systems.

SUMMARY OF THE INVENTION

Accordingly, the present invention provides an improved activesuspension system for a work vehicle. The improved suspension systemincludes a control circuit which communicates via a communicationinterface to other vehicle systems which are the source of vibrations.The system includes an active vibration isolator responsive to controlsignals generated at least partly in response to parameters of the othersystems which relate to forces applied to the vehicle during operationof those systems. The system can react to draft forces generated by aplow, normal forces which occur during steering, clutch forces generatedas a clutch engages and disengages, gear shift forces generated by atransmission, braking forces due to braking and acceleration forces dueto speed changes.

One embodiment of the invention relates to an active suspension systemfor a work vehicle. The work vehicle includes a chassis, an operator'scab and another vehicle system having a parameter related to a forceapplied to the work vehicle. The suspension system includes an activevibration isolator located between the cab and the chassis andresponsive to a control signal to control movement of the cab relativeto the chassis, a communication interface coupled to the another vehiclesystem, and a control circuit configured to receive the parameter of theanother vehicle system from the communication interface, to generate thecontrol signal at least partly in response to the parameter, and toapply the control signal to the vibration isolator to attenuate movementof the cab due to the force. Such a system can also be mounted betweenthe cab and operator's seat, or between the wheels and the chassis.

Another embodiment of the invention relates to a work vehicle includinga chassis, an operator's cab, an active suspension system including atleast one active vibration isolator mounted between the cab and chassisand responsive to a control signal to control movement of the cabrelative to the chassis, another vehicle system having a parameterrelated to a force applied to the work vehicle, and a communicationinterface coupled between the suspension system and the another vehiclesystem. The system further includes a control circuit configured toreceive the parameter of the another vehicle system, to generate thecontrol signal at least partly in response to the parameter, and toapply the control signal to the active vibration isolator to attenuatemovement of the cab due to the force.

Another embodiment of the invention relates to an active suspensionsystem for a work vehicle. The work vehicle includes a chassis, anoperator's cab disposed above the chassis, and a second vehicle systemhaving a parameter related to ground speed of the work vehicle. Theactive suspension system includes at least one active vibration isolatormounted at a location between the cab and the chassis and responsive toa control signal to control movement of the cab relative to the chassis,a communication interface coupled to the second vehicle system, and acontrol circuit configured to receive the parameter of the secondvehicle system from the communication interface, to generate the controlsignal applied to the isolator to attenuate movement of the cab when theground speed is above a predetermined speed threshold, and to disablecab movement when the ground speed is below the threshold.

BRIEF DESCRIPTION OF THE DRAWINGS

The invention will become more fully understood from the followingdetailed description, taken in conjunction with the accompanyingdrawings, wherein like reference numerals refer to like parts, in which:

FIG. 1 shows a work vehicle (e.g., an agricultural tractor) equippedwith an active cab suspension system which includes two front and onerear active vibration isolators located between the vehicle's cab andchassis;

FIG. 2 is a schematic rear view of the work vehicle shown in FIG. 1;

FIG. 3 is a view from the side of the work vehicle of one of the frontactive vibration isolators which includes electrical interfaces to anaccelerometer, a displacement sensor, a load sensor, a pressure sensorand a hydraulic actuator, a hydraulic interface to the actuator, and apneumatic interface to an air spring;

FIG. 4 is an exploded view of the accelerometer mounting assembly shownassembled in FIG. 3;

FIG. 5 is a cross-sectional view of the coupling between theaccelerometer and the actuator's piston;

FIG. 6 is a view from the rear of the work vehicle of the rear activevibration isolator which includes two springs to support the weight atthe rear suspension point;

FIG. 7 is a mechanical schematic of the active vibration isolator shownin FIG. 3;

FIG. 8 is a schematic diagram of the active cab suspension system inFIG. 1 including connections between the electrical, hydraulic andpneumatic interfaces of the active vibration isolators and a controller,pressurized hydraulic fluid source and pressurized air source;

FIG. 9 is a schematic block diagram of the active suspension controllerof FIG. 8 which includes a data bus interface for communicating withother vehicle systems;

FIG. 10 is a process flow control diagram for the hydraulic actuator ofeach active vibration isolator;

FIG. 11 is a schematic block diagram representing interconnectionsacross a vehicle data bus between the active suspension controller andother vehicle systems;

FIG. 12 is a block diagram of the positioning control system in FIG. 11which includes a GPS receiver, memory card interface, and positioningcontrol circuit;

FIG. 13 is a table representing a predetermined geo-referenced mapincluding spatially-variable data indicative of altitudes and bumpinesslevels;

FIG. 14 represents a predetermined geo-referenced map of a road and afield which includes bumpiness level data; and

FIG. 15 shows a work vehicle equipped with another embodiment of anactive cab suspension system including an active isolator locatedbetween a side of the cab and a vertical support member (eg., enginecompartment wall).

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

Referring to FIGS. 1 and 2, a work vehicle 2 (e.g., an agriculturaltractor) includes a frame or chassis 4, an operator's cab 6 supportedabove chassis 4, a seat or dual seats 8 within cab 6, and a propulsionsystem 10 to propel vehicle 2 along a ground surface 12 in a forwarddirection 14. Propulsion system 10 includes an engine 16 secured tochassis 4, a transmission (not shown) coupled to engine 16, two drivenor non-driven front wheels 18 steered by a steering wheel 20, and tworear wheels 22 driven by engine 16 via the transmission. Brake pedals 24located in cab 6 operate left and right service brakes (not shown) toprovide braking. Cab 6 is supported above chassis 4 by an active cabsuspension system (ACS) 26 including two front active vibrationisolators 28 and 30 located on opposite sides of cab 6 and a rearisolator 32 centrally located at the rear of cab 6 between wheels 22.The three-point suspension system provides stable control of movementresponsive to pitch, roll and bounce.

In some work vehicle applications, ACS 26 includes a forward-lookingsensor 34 mounted to vehicle 2 to detect the bumpiness level on surface12 forward of vehicle 2. Sensor 34 may include a radar to detectbumpiness based on the time needed for electromagnetic signals to travelfrom sensor 34 to surface 12 and be reflected back. However, sensor 34could also include a vision-based or proximity sensor (e.g., amicropower impulse radar (MIR) device). Sensor 34 is mounted to vehicle2 at a location oriented toward surface 12. For example, sensor 34 maybe mounted on the hood of vehicle 2 (34a), or mounted below vehicle 2 todetect bumpiness forward of rear wheels 22 (34b), or mounted forward offront wheels 18 (34c). The sensed signals represent general levels ofbumpiness (e.g., a smooth or rough surface) and are used to adjustperformance parameters of isolators 28-32.

In some work vehicle applications, ACS 26 includes a leveling sensor 36mounted to cab 6 to generate signals indicative of the degree to whichthe attitude of cab 6 is level relative to horizontal. Leveling sensor36 may include a gyroscope or electronic level signal generator, andsensor 36 may be mounted at the center of gravity of cab 6. The signalfrom sensor 36 can be used to control the attitude of cab 6 and tomaintain a level attitude.

ACS 26 may further include a movement sensor 37 (e.g., a three-axisaccelerometer) mounted adjacent to an operator's torso or head (e.g.,supported by a headrest of seat 8) to accurately sense the movement feltby the operator. The signal from sensor 37 is used as a primary orsecondary control input to more accurately control the movement of cab 6and its affect on the operator. ACS 26 may also include severalaccelerometers mounted to cab 6. These signals are combined to form acontrol input.

Components of other vehicle systems within cab 6 may include a steeringangle sensor 38 coupled to wheel 20 to generate a signal representingsteering angle, and brake detecting circuits 39 coupled to brake pedals24 to detect application of the service brakes. Circuits 39 can also becoupled directly to the brakes. The signals generated by sensor 38 andcircuits 39 are supplemental control inputs used by ACS 26 to counteractmovement of cab 6 due to forces applied to chassis 4 when turning orbraking, or are used as preparatory signals (e.g., to bias the hydraulicfluid supply toward the particular isolator which will require thefluid).

As explained below, ACS 26 attenuates transmission of vibrations betweenchassis 4 and cab 6 caused by the interaction of wheels 18 and 22 withsurface 12, or due to forces applied to vehicle 2 during operation ofother vehicle systems such as the steering, transmission and brakingsystems. Each isolator 28-32 can be controlled separately, orcoordinated with each other to improve vibration isolation and toprovide additional functions. Coordinated control of isolators 28-32 canprovide improved response to pitch, roll and bounce forces applied tocab 6. Performance parameters of ACS 26 are adjustable in response toestimated conditions ahead of vehicle 2, or to changes in load. Thegain, and thus the frequency response, of ACS 26 is set to maximize thevibration isolation of ACS 26 without exceeding the mechanical limits(i.e., actuator stroke) of the system. The gain can further be tunedmanually to account for differences among the frequency response ofindividual operators.

Although a tractor is shown in FIGS. 1 and 2, ACS 26 may be used withother agricultural work vehicles such as combines or cotton-pickers orwith construction vehicles such as backhoes, cranes, dozers, trenchers,skid-steer loaders, etc. These vehicles may be equipped with eitherwheeled or tracked propulsion systems. Other arrangements of ACS 26 canbe used in these vehicles such as a three-point active suspension systemincluding one front and two rear isolators or a four-point system withtwo front and two rear isolators. Further, one or more active vibrationisolators 28-32 can be mounted between cab 6 and seat 8 in an activeseat suspension system.

Referring to FIG. 3, front active vibration isolator 28, which issubstantially the same as front isolator 30, includes lower and uppermounts 40 and 42, respectively, which are attached to chassis 4 and cab6, respectively, by welding, screws, bolts or other fasteners. A spring44 including an air bag is connected between mounts 40 and 42 to supportthe static weight of cab 6. Spring 44 includes an enclosure 46comprising a cylindrical outer casing 48 attached (e.g., welded) tolower mount 40 and a cylindrical inner casing 50 attached to upper mount42 and extending into outer casing 48. The air bag (not visible) issecured within enclosure 46. The air bag is inflated with pressurizedair through a supply tube 52 and a pneumatic fitting 54 to a pressuresufficient to support the static weight of cab 6 so as to off-load theweight from other components of isolator 28.

In some work vehicle applications, the air pressure in springs 44 is setat a constant level to support the static weight of cab 6, and thepressure is not adjusted to account for changes in load of cab 6 onisolators 28-32. In such applications, a pneumatic system is chargedwith pressurized air supplied to spring 44 through tube 52. The pressureof the air supplied to spring 44 is set or regulated at or slightlybelow the pressure needed to raise cab 6. Solenoid-controlled valvesturn on the flow of air to isolators 28-32. Such systems may bepressurized off-line so the vehicle does not require an on-board aircompressor. Alternatively, air pressure in such pneumatic systems may bemaintained by an on-board air compressor to replace air lost to leaks.This type of system does not actively control air pressure, and does notrespond to changes in the weight of cab 6.

However, in other work vehicle applications, ACS 26 actively controlsthe air pressure within springs 44. As described below, such systemsinclude air control valves to selectively supply and relieve pressurizedair from a source (e.g., a compressor and/or high pressure air tank) tosprings 44 in response to control signals generated based on, forexample, load forces exerted on springs 44 by cab 6. The compressed airsource provides the ability to actively control pressure duringoperation of vehicle 2. To improve accuracy in controlling pressure, thepressure in springs 44 may be monitored using a pressure sensor 56mounted to upper mount 42 and configured to generate closed-looppressure feedback signals on conductors 58.

Isolator 28 includes a rollover restraint system 60 to prevent cab 6from detaching from chassis 4 during a rollover. Restraint system 60includes a rollover frame 62 secured (e.g., welded) to lower mount 40which is able to cooperate with a plate 64 secured to outer casing 48.Frame 62 includes a circular hole 66 having a diameter slightly largerthan that of casing 48 but less than that of plate 64. In the event of arollover causing casing 48 to separate from lower mount 40, casing 48can slide upward within hole 66 until plate 64 makes contact with frame62. Thus, movement of cab 6 caused by a rollover is restrained and cab 6does not detach from chassis 4.

Connected adjacent to spring 44 between mounts 40 and 42 is a linearhydraulic actuator 68. Actuator 68 includes a cylinder 70 and a pistonor rod 72 moveable therein to move cab 6 relative to chassis 4. A valveassembly 74 coupled to cylinder 70 selectively supplies and relievespressurized hydraulic fluid between a pair of tubes 76 and 78 andcylinder 70 in response to valve control signals received on conductors80. Thus, piston 72 moves in either direction along the axis of cylinder70 in response to the control signals. Preferably, the control signalsare pulse-width modulated (PWM) control signals and valve assembly 74 isa four-way, three-position electrically-controlled solenoid valve.

Referring to FIGS. 3-5, a threaded free end 82 of piston 72 extendsthrough upper mount 42 and is coupled to a movement sensor 84 via amounting assembly 86 which provides high-frequency isolation of sensor84 from mount 42. In upward order, assembly 86 includes aninternally-threaded rod nut 88 for receiving end 82, a potentiometertarget bracket 90 having an aperture 92, a lower hardened washer 94having an aperture 96, an elastomeric vibration isolator 97 having lowerand upper isolator portions 98 and 100 located on opposite sides ofupper mount 42 and having apertures 102 and 104, an upper hardenedwasher 106 having an aperture 108, and a bolt/sleeve 110 having athreaded bore 112 to securely receive free end 82 of piston 72. Isolatorportions 98 and 100 include inner annular portions 114 and 116,respectively, which pass through an aperture 118 in mount 42. Thecomponents of assembly 86 are coaxially aligned such that piston 72passes through nut 88, apertures 92, 96, 102, 118, 104 and 108 and bore112. Thus, elastomeric vibration isolator 97 physically separates uppermount 42 from piston 72 to provide high-frequency isolation.

Bolt/sleeve 110 includes a tapped hole 120 coaxial to piston 72 toreceive a threaded post 122 of movement sensor 84, thereby securelymounting sensor 84 to piston 72. Sensor 84 generates an electricalsignal on conductors 124 which represents movement of piston 72 in adirection along the axis of piston 72 at a point P (e.g., at washer 94)lying between actuator 68 and elastomeric isolator 97. Thus, isolator 97provides high-frequency isolation between upper mount 42 and movementsensor 84. Sensor 84 preferably includes an accelerometer. Duringoperation, valve control signals generated in response to the signalsfrom sensor 84 are applied to actuator 68 to move cab 6 to counteractthe movement of chassis 4. Post 122 can alternatively be secureddirectly to a bore in end 82 of piston 72.

Potentiometer target bracket 90 includes first and second flat portions126 and 128 and a rising portion 130 extending from portion 126 to 128.A displacement sensor 132 (e.g., potentiometer; inductive sensor) isadjustably secured by bolts 134 to a track 136 running along valveassembly 74. Sensor 132 generates electrical signals on conductors 138representing the distance that actuator shaft 140 extends from casing142. This distance is indicative of the displacement between mounts 40and 42. The displacement signal from sensor 132 is used to bias piston72 to a centered steady-state position so as to prevent migration toeither end of cylinder 70 over time, and to control the height of cab 6above chassis 4.

Vibration isolator 28 may also include a load sensor 144 which generateselectrical signals on conductors 146 representing load forces exerted bycab 6 on chassis 4. The load forces can be used to adjust air pressurewithin spring 44 to account for changes in weight of cab 6. For example,changes in the weight of an operator, or changes due to having twopeople in cab 6, can be accommodated.

To accommodate translational movement between chassis 4 and cab 6, aspherical bearing assembly 148 is provided between cylinder 68 and lowermount 40. Assembly 148 includes a bearing eye 150 which extends downfrom cylinder 68 and encompasses a spherical bearing 152. Eye 150 fitsinto a slot within a bearing block 154 mounted to lower mount 40, and isheld in place by a crosspin 156 inserted through an aperture in block154 and bearing 152. Assembly 148 allows relative movement of cylinder68 about the axis of bearing 152.

Although FIG. 3 shows actuator 68 adjacent to spring 44, actuator 68 andspring 44 may be coaxially located as shown in U.S. Pat. No. 5,603,387,herein incorporated by reference in its entirety.

Referring to FIG. 6, rear isolator 32 is similar to front isolator 28except that rear isolator 32 includes a second spring 44 to off-load thehigher static weight of cab 6 on rear isolator 32. Off-loading may benecessary to avoid exceeding the weight capacity of a single air bag.However, a second spring may not be needed if ACS 26 includes fouractive isolators, or if the cab weight does not exceed the capacity of asingle air bag. Other differences between rear isolator 32 and frontisolator 28 include the shapes of potentiometer target bracket 90 and ofupper mount 42 (which both extend between springs 44), and the couplingof elastomeric vibration isolator 97 to bracket 90 instead of to uppermount 42. Sensor 132 is mounted on or within cylinder 70 such thatsensor 132 and cylinder 70 are co-linear.

Referring to FIG. 7, each vibration isolator 28-32 is represented by amechanical schematic showing spring 44 connected between cab 6 andchassis 4, actuator 68 connected between chassis 4 and point P (e.g., atwasher 94), and elastomeric vibration isolator 97 in series withactuator 68 between point P and cab 6. Actuator 68 provides lowfrequency (e.g., below 20 Hz) isolation between chassis 4 and point P.Isolator 97 provides high frequency (e.g., above 20 Hz) isolationbetween point P and cab 6. Thus, cab 6 is isolated from chassis 4 forboth high and low frequency movement or vibrations.

Each individual active vibration isolator 28-32 has characteristicsdefined by the mass M of cab 6 supported by the isolator, the stiffnessK_(s) of spring 44, the input velocity V_(C) of actuator 68, andstiffness K and damping coefficient R of isolator 97. Stiffness K_(S) ofspring 44 affects only the power consumption of actuator 68 and does notaffect idealized isolation. The quantity being actively controlled isinput velocity V_(C) of actuator 68.

Referring to FIG. 8, ACS 26 includes front isolators 28 and 30, rearisolator 32, an active suspension system controller (ASC) 200, a sourceof pressurized hydraulic fluid 202, a pressurized air source 204, an aircontrol valve 206 for each isolator 28-32, and a vehicle data bus 208.ASC 200 is connected by electrical conductors to movement sensor 84,displacement sensor 132, load sensor 144, air pressure sensor 56, valveassembly 74, and air control valve 206 of each isolator 28-32, and tobump sensor 34, leveling sensor 36, and movement sensor 37. ASC 200receives signals from each sensor and generates output signals inresponse thereto which are applied to valves 74 and 206. ASC 200 furthercommunicates to and from other vehicle systems via bus 208. Preferably,bus 208 conforms to the SAE J-1939 standard for vehicle data bussesentitled "Recommended Practice for a Serial Control and CommunicationsVehicle Network".

Pressurized hydraulic fluid source 202 includes an engine-driven pump210 to supply pressurized hydraulic fluid to isolators 28-32 via tubes76 under the control of valve assemblies 74. Valve assemblies 74 alsocontrol release of fluid from isolators 28-32. Released fluid isreturned to a reservoir 212 of source 202 via tubes 78.

When pressure in springs 44 is actively controlled, each air controlvalve 206 includes an apply valve 214 which receives a flow ofpressurized air from source 204 (e.g., a compressor) and selectivelyapplies the flow to spring 44 of each isolator 28-32 in response tocontrol signals generated by ASC 200. Each valve 206 includes a releasevalve 216 to selectively release air from the air bag to a vent 218 inresponse to the air control signals. The pressure within each air bagincreases up to the maximum pressure of source 204 when the apply valve214 is open, and decreases when release valve 216 is open. The aircontrol signals may include PWM signals.

Referring to FIG. 9, ASC 200 includes a signal conditioning/multiplexercircuit 220 to receive signals from sensors 84, 132, 144 and 56 of eachisolator 28-32 and from sensors 34, 36 and 37. ASC 200 further includesan active suspension control circuit (ASCC) 222 coupled to circuit 220,a memory circuit 224 accessible to ASCC 222, an interface circuit 226 togenerate control signals (e.g., PWM signals) to valve assembly 74 andair control valve 206 associated with each isolator 28-32, and a databus interface circuit 228 configured to communicate with other vehiclesystems across bus 208.

Circuit 220 includes signal conditioning hardware (e.g., filters),multiplexers and A/D interface circuits. ASCC 222 includes a digitalprocessor (e.g., a 16-bit microprocessor) which may include softwareconditioning such as digital filtering or averaging. Memory circuit 224includes nonvolatile memory (ROM, EEPROM or FLASH) for storing programsand volatile memory (RAM) for storing variables. Dedicated, specificpurpose equipment or hard-wired logic circuitry can also be used. PWMinterface circuit 226 generates PWM control signals based upon digitalwords written to circuit 226 by ASCC 222. Interface circuit 228 formatsinput and output bus messages which conform to the J-1939 standardprotocol.

ASC 200 includes an operator interface circuit to receive commandsignals from operator-actuatable command devices and control operationof ACS 26. The interface includes a signal conditioning/multiplexercircuit 230 (which may be the same as circuit 220) which receivessignals from command devices 232-238. Devices 232-238 include any or allof: a cab rate command device 232 (e.g., potentiometer) to set a rate atwhich cab 6 moves during power-up/power-down; a cab height commanddevice 234 (e.g., potentiometer) to set a steady-state height of cab 6above chassis 4; a cab lower command device 236 (e.g., switch) tocommand cab 6 to a minimum height; and a tuning device 238 (e.g.,potentiometer) to tune the gain, and thus the frequency response, of ACS26.

Referring to FIG. 10, ASC 200 generates the valve control signalsapplied to actuator 68 via conductors 80 for each active vibrationisolator 28-32. The control signals may be generated individually foreach isolator 28-32 using the process shown in FIG. 10. The inputs tothe process are displacement signal D (FIG. 7) sensed by sensor 132, andacceleration signal A (FIG. 7) sensed by sensor 84. A first network 240having the shown transfer characteristics removes a DC component ofsignal A caused by the acceleration of gravity and integrates signal Ato generate a signal representing absolute velocity at point P (FIG. 7).A second network 242 provides dynamics to isolate lower vibrationfrequencies (e.g., below 20 Hz) with desired stability and performancecharacteristics. Second network 242 can be tuned to the resonantfrequency of chassis 4, or to a frequency selected by the operator. Asumming circuit 244 sums the output from network 242 with signal D toproduce a combined signal representing both the velocity of chassis 4 tobe counteracted and the displacement of piston 72. Signal D causespiston 72 to return to a centered steady-state position to prevent themigration of piston 72 to either end of cylinder 70 over time. A gaincircuit 246 amplifies the summed signal and applies the amplified signalto PWM interface circuit 226 to generate the valve control signalsapplied to hydraulic valve 74. Valve 74 responds by selectivelysupplying and relieving hydraulic fluid to each actuator 68 to causeeach piston 72 to move cab 6 relative to chassis 4.

Thus, the transmissibility of each isolator 28-32 is defined by theequation:

    V.sub.O /V.sub.I =1/(1+G)*((R/M)s+K/M)/(s.sup.2 +(K/M)s+K/M)

wherein G is the gain (e.g., 100) of circuit 246 relating input velocityV_(C) of actuator 68 with the velocity at point P, V_(O) is the velocityof cab 6 (FIG. 7), V_(I) is the velocity of chassis 4 (FIG. 7), R and Kare the damping coefficient and stiffness of elastomeric isolator 97,and M is the mass of cab 6 being supported. The gain G of circuit 246may be adjusted manually by an input device such as a potentiometer (notshown), or automatically as described below. Stiffness K_(S) of spring44 does not affect transmissibility because spring 44 only off-loads thestatic weight of cab 6 to reduce power consumption.

In work vehicle applications wherein air pressure within air springs 44is actively controlled, ASC 200 generates the control signals applied tothe air control valve 206 of each isolator 28-32 to selectively supplyand relieve pressurized air to the air bags. The control signals controlthe air pressure within springs 44 in response to load signals generatedby load sensors 144. The pressure within springs 44 is controlled tosupport the static weight of cab 6 on each isolator 28-32. Thus, changesin weight of cab 6 at each support position are accommodated by changesin pressure within each spring 44. Closed-loop pressure control can beprovided using pressure signals from sensors 56 as feedback signals.

The control process shown in FIG. 10 and the active control of pressurewithin springs 44 can be modified to adjust performance parameters ofACS 26. The adjustable parameters include, for example, the gain andfrequency response of isolators 28-32, and the gain at which thedisplacement signal from sensor 132 biases piston 72 to the steady-stateposition to prevent migration of piston 72 to either end of cylinder 70over time. The gain of isolators 28-32 is adjusted by changing gain G ofcircuit 246, or the gain of network 240 or 242 (e.g., gain G₁). Thefrequency response is adjusted by modifying the transfer function ofnetwork 242. The gain at which piston 72 is biased is adjusted bychanging the impact of signal D in the control process of FIG. 10. Forexample, the impact is changed by adjusting the weight of signal D inthe combined signal output by summing circuit 244. As discussed above,the pressure within springs 44 is also an adjustable parameter which canbe actively controlled.

The primary control inputs for ACS 26 include the acceleration signal Aand displacement signal D. The system is set to provide maximum gainwithout exceeding the stroke of actuators 68. However, the gain may thenbe adjusted based on secondary or supplemental control inputs such asestimated conditions or signals from other vehicle systems. Onesupplemental input used to adjust the performance parameters of ACS 26is the estimated condition of surface 12 forward of vehicle 2. Adaptiveor predictive control algorithms respond to the estimated condition toimprove performance. For example, the performance parameters may beadjusted based upon the estimated bumpiness of surface 12 ahead ofvehicle 2. Bumpiness may be estimated by processing (e.g., taking aroot-mean-square of) the signals from bump sensor 34. Alternatively, thebumpiness level can be estimated from the previous level of movementsensed by movement sensor 84 based upon the assumption that surface 12forward of vehicle 2 will have a similar bumpiness level as surface 12behind vehicle 2.

The bumpiness level can also be estimated based upon the assumptionsthat vehicle 2 travels quickly on roads and slowly in fields, and thatroads are smooth while fields are bumpy. The level is estimated bycomparing ground speed of vehicle 2 to a predetermined threshold speed(e.g., 10 mph). High velocities correspond to a smooth bumpiness level,while low velocities correspond to a rough bumpiness level. Othermethods of estimating bumpiness based upon the positions of vehicle 2and geo-referenced maps of surface 12 are described below.

When the estimated signals represent a bumpiness level, the valvecontrol signals applied to actuator 68 attenuate movement of cab 6 dueto movement of chassis 4 in response to the bumpiness level by adjustingthe gain of ACS 26. If surface 12 has a high bumpiness level, ASC 200lowers the gain G of circuit 246 such that piston 72 is not commandedbeyond its maximum stroke. However, if surface 12 has a low bumpinesslevel, ASC 200 raises the gain G to increase isolation provided byisolators 28-32. The degree at which gain is adjusted may depend uponthe level of bumpiness if there are more than two levels.

The gain at which the sensed displacement causes cab 6 to move towardthe centered steady-state position can be decreased when surface 12 isrelatively bumpy to help insure that piston 72 has sufficient stroke torespond to the bumps as they occur. This gain may be increased whensurface 12 is smooth to provide a smoother ride. Also, the frequencyresponse of isolators 28-32 may be changed based on estimated bumpinessif empirical tests indicate that such an adjustment would increase ridequality. The frequency response may also be adjusted manually by theoperator using signals from tuning device 238.

ASC 200 can control each active vibration isolator 28-32 independently.Independent control, however, does not provide functions which areachieved or optimized only through coordinated control. Thus, the valvecontrol signals applied to actuators 68 and air control signals appliedto air control valves 206 are coordinated with each other to coordinatecontrol of isolators 28-32.

In some work vehicle applications, the valve control signals applied toactuators 68 are coordinated with each other to coordinate control ofthe displacements between chassis 4 and cab 6 at the locations ofisolators 28-32. A benefit of coordinating the displacements can beseen, for example, during power-up and power-down of vehicle 2.

Assume that actuator 68 of each isolator 28-32 is controlled using anindependent controller. At power-up, the static weight of cab 6 is justsupported by springs 44 and pistons 72 are in their power-down positions(eg., maximum downward or retracted positions). Then, as eachindependent controller enters an actuator control loop after completinginitialization logic (e.g., built-in tests), the valve control signalscause each actuator 68 to raise cab 6 until each respective piston 72reaches an operating position (e.g., its centered steady-stateposition). Each actuator 68 will raise cab 6 with random timing andrates compared to other actuators 68 due to differences in timing foreach controller to enter its actuator control loop, and differences intiming for the vehicle hydraulic system to provide pressurized hydraulicfluid to each actuator 68. The random timing and rates with which cab 6is raised on power-up causes jerking and uneven cab attitudes which arefelt by the operator. A similar problem occurs during power-down ofvehicle 2.

In response to these problems, ASC 200 coordinates control signalsapplied to each isolator 28-32 to control the attitude and movement rateof cab 6 during power-up and power-down. At power-up, ASC 200 performsbuilt-in tests and other initialization functions. Then, ASC 200 raisescab 6 to a steady-state height while maintaining cab 6 at asubstantially constant or level attitude by coordinating the commandsignals applied to valves 74 and using sensed displacement signals asclosed-loop feedback signals. Equalized commands are simultaneouslyapplied to valves 74 to extend each piston 72 from its power-downposition to its steady-state position at a predetermined rate. The ratecan be fixed, or can be manually set by cab rate command device 232. Toinsure availability of sufficient hydraulic power to each isolator28-32, ASC 200 delays extending pistons 72 until a sufficient time haspassed following power-up. Alternatively, ASC 200 can monitor thedisplacement of each isolator 28-32 and set the command signals toextend pistons 72 no faster than the movement of the slowest isolator28-32. Thus, no isolator is raised faster than another isolator whichmay lag due to insufficient hydraulic power. Closed-loop displacementcontrol is also performed during power-down.

In one embodiment, ASC 200 includes control logic which prevents cab 6from being actively moved relative to chassis 4 when vehicle 2 is notmoving (i.e., ground velocity less than a predetermined speed threshold)or when an operator-presence sensor indicates the operator is notpresent. For example, ASC 200 does not raise cab 6 to its steady-stateheight until vehicle speed exceeds a threshold. Gating the valve controlsignals with movement of vehicle 2 prevents the unexpected movement ofcab 6 when a person outside cab 6 is nearby. Vehicle speed can be sensedusing sensor 338 (FIG. 12).

Another benefit of coordinating the displacements is the ability tocontrol the attitude of cab 6, either with respect to the horizontal(i.e., horizon) or with respect to chassis 4. For example, to maintain alevel attitude of cab 6 with respect to chassis 4, displacement signalsfrom each sensor 132 can be combined (e.g., averaged) and the combinedsignal used as the steady-state displacement control parameter (e.g., Din FIG. 10). Further, if work vehicle 2 is equipped with leveling sensor36, the steady-state displacement control parameter can depend on thesignal from sensor 36 to maintain a level attitude of cab 6 with respectto the horizontal. For example, if a sensed signal indicates that thefront of cab 6 is tilting downward, the displacement of front isolators28-30 can be increased and the displacement of rear isolator 32decreased to level the attitude of cab 6. Sideways adjustments can bemade when cab 6 is tilting sideways. The changes to the steady-statedisplacements that are made to control the attitude of cab 6 are limitedto a portion of the stroke of piston 72 such that piston 72 retains theability to provide vibration isolation.

The steady-state height of cab 6 above chassis 4 can also be adjustedmanually using cab height command device 234. Further, the height of cab6 can be lowered to a minimum level in response to an actuation of lowercommand device 236 (for example, to decrease the clearance required forvehicle 2 to pass beneath an overhang).

The valve control signals may also be coordinated with each other tocoordinate the attenuated transmission of force between cab 6 andchassis 4. For example, as explained above, the performance parametersof isolators 28-32 may be adjusted during operation of vehicle 2. Itmay, however, be undesirable for each isolator 28-32 to have differentparameter values. Thus, the parameters of each isolator 28-32 may beadjusted to the same parameter values by, for example, averaging theindividually-determined parameter values for each isolator 28-32.

In some work vehicle applications, the control signals applied to aircontrol valves 206 are coordinated with each other to coordinate controlof air springs 44. As described above, the air pressure within eachspring 44 can be actively controlled to just support the static weightof cab 6 on each isolator 28-32 so that actuators 68 are able to movecab 6 with minimal power consumption. However, the total weight of cab 6may change due to, for example, changes in weight of the operator oroperators, or storage or removal of objects (e.g., tools). Further, evenassuming a constant total cab weight, the relative weight of cab 6 onisolators 28-32 depends on the slope of surface 12, regardless ofwhether vehicle 2 is still or is moving. For example, when vehicle 2 ison a slope, the weight supported by a downward isolator increases andthe weight supported by an upward isolator decreases. Withoutadjustment, the air pressure in each spring 44 will no longer becorrect, and actuator 68 will consume extra power to counteract thechanged effective weight.

Changes in load force exerted on each isolator 28-32 due to a change intotal weight of cab 6 are accommodated by sensing load force on eachisolator 28-32, summing the signals to determine a total load force, anddistributing the total load force among isolators 28-32 using a knownformula based upon the configuration of isolators 28-32. For example, iftotal load force corresponds to a weight of 2000 pounds, ASC 200 mayattribute 500 pounds to each front isolator 28-30 and 1000 pounds torear isolator 32. The air pressure in the respective springs 44 wouldthen be set to support these weights. Thus, the load forces will bedistributed correctly even if vehicle 2 is on a steep grade when themeasurements of load force are taken (which would cause incorrectresults if the air pressure of each isolator 28-32 was set independentlybased upon the sensed load force of that isolator). Total load force ispreferably sensed when vehicle 2 is still (e.g., at power-on or whenvehicle velocity is 0) to prevent movements of cab 6 from affecting thesensed signals.

Changes in the relative weight of cab 6 on each isolator due to changesin ground slope during operation are accommodated by distributing thetotal load force of cab 6 (determined on power-on or when vehiclevelocity is 0) to isolators 28-32 in one of two manners. (Note that theabsolute load signals generated by sensors 144 may be inaccurate whenvehicle 2 is moving.) First, the total load force can be distributedamong isolators 28-32 based on the attitude of cab 6 sensed by levelingsensor 36. For example, if the front of cab 6 is tilted downward, theair pressure in front isolators 28-30 is increased and the air pressurein rear isolator 32 is decreased. Second, the load signals fromisolators 28-32 can be summed and the total load force (measured whenvehicle 2 was still) distributed to each isolator 28-32 based upon therelative contribution to the summed signal of that isolator's loadsignal. The air control signals for each isolator 28-32 are thengenerated based upon the distributed load force.

Thus, by coordinating the air control signals to distribute the totalload force among isolators 28-32, changes in weight of cab 6 areaccommodated accurately even when vehicle 2 is on a sloped surface ormoving.

When work vehicle 2 is equipped with a vehicle data bus, ACS 26communicates via the bus with other vehicle systems having parametersrelated to forces which will be applied or are being applied to vehicle2. Movement of cab 6 due to such forces is attenuated by appropriatecontrol of isolators 28-32 as explained below. Control input signalsfrom such other vehicle systems are supplemental inputs for ACS 26, andthe acceleration signals remain the primary control inputs.

Referring to FIG. 11, an exemplary vehicle control system 250 showsvehicle 2 equipped with ASC 200 and with other vehicle control systemsin communication with each other via bus 208. Vehicle control system 250includes an armrest console control system 252 coupled to armrestconsole input devices 254 to receive command signals, and a positioningcontrol system 256 to receive positioning signals representing locationsof vehicle 2. Although command devices 232-238 are wired to ASC 200 inFIG. 9, these command devices may also be located in the armrest consolewhere they are read by control system 252.

Control system 250 includes other vehicle systems having parametersrelated to forces applied to vehicle 10. For example, control system 250may include a tool height control system 258, a steering control system260, a four-wheel drive/differential lock (4WD/DL) control system 262,and a transmission and speed control system 264. Each system 258-264includes input devices 266 to generate command signals and outputinterfaces 268 to control output actuators. Vehicle 2 may be equippedwith any or all of these systems (e.g., a tractor equipped with toolheight control system 258 may not have an armrest control consolecoupled to bus 208). Vehicle 2 may also include other vehicle systemshaving parameters related to forces applied to vehicle 2. Communicationof parameters related to forces applied to vehicle 2 across bus 208gives ASC 200 access to such parameters without the need for separatesensors dedicated to ACS 26.

In one embodiment, tool height control system 258 is installed on atractor equipped with a hitch assembly to raise and lower a tool (e.g.,implement or plow). Input devices 266 include draft force and positioncommand devices used by control system 258 to generate control signalsapplied to an actuator to raise and lower the tool. Sensors providedraft force and position feedback signals. The command signals generatedby input devices 266 are indicative of draft forces which will beapplied to the tractor, and the feedback signals are indicative of draftforces currently being applied to the tractor. Thus, the command signalsand feedback signals are both related to draft forces applied to thetractor. A hitch assembly control system for a tractor having the abovecomponents is described in U.S. Pat. No. 5,421,416. In anotherembodiment, tool height control system 258 is installed on a combineequipped with a positioning assembly which raises and lowers a header. Aheader control system for a combine is described in U.S. Pat. No.5,455,769. The '416 and '769 patents are commonly assigned and hereinincorporated by reference.

Steering control system 260 includes a steering input device 266 (e.g.,steering wheel 20) coupled to a sensor (e.g., sensor 38) which generatessteering angle command signals indicating the degree of turning. Afeedback sensor can be used to measure actual turning. The sensedsignals are indicative of the normal forces applied to vehicle 10 due toturning since steering angle is a measure of turning radius, and normalforce equals velocity squared divided by radius. Velocity is sensed by aground speed sensor such as sensor 338. A steering control system isdisclosed in U.S. Pat. No. 5,194,851, commonly assigned and hereinincorporated by reference.

An exemplary 4WD/DL control system 262 is described in U.S. Pat. No.5,505,267, commonly assigned and herein incorporated by reference.Control system 262 includes 4WD/DL input devices 266 and outputinterfaces 268, and has parameters indicative of command and outputsignals for a 4WD clutch and DL lock related to forces applied tovehicle 2 as 4WD is engaged and disengaged and DL is locked andunlocked. The '267 patent further discloses brake detecting circuits(e.g., circuits 39) coupled to the brakes (e.g., brakes 24) of a vehicleto generate signals representing the state of the brakes and, thus,whether braking forces are being applied to vehicle 2.

An exemplary transmission/speed control system 264 is described in U.S.Pat. No. 5,233,525, also commonly assigned and incorporated herein byreference. Control system 264 includes gear shift and speed inputdevices 266 and output interfaces 268. Control system 264 has parametersindicative of commanded and output gear shift signals of a transmission,and commanded and output speed actuator settings. These parameters arerelated to the forces applied to vehicle 2 as the transmission upshiftsand downshifts and vehicle 2 accelerates and decelerates.

ASC 200 has access via bus 208 to parameters of the other systems shownin FIG. 11 related to forces applied to vehicle 2 during operation ofthose systems. ASC 200 uses the parameters as supplemental controlinputs when generating control signals for isolators 28-32 to attenuatemovement of cab 6 due to such forces. For example, if a parameterindicates that a pitch or normal force is about to be applied to vehicle2 control signals applied to isolators 28-32 will prevent the operatorfrom being thrown backwards or sideways. The gain parameter can also beadjusted when such forces are predicted. Further, the attitude of cab 6can be changed to improve ride quality in response to such forces (e.g.,by tilting cab 6 into a turn, or tilting cab 6 in the fore-and-aftdirection in response to a pitch force). In addition, the forceparameters from other vehicle systems can be used by ACS 26 aspreparatory signals. For example, ACS 26 could bias the oil supply tothe isolator 28-32 which will require the most oil flow when the forceactually impacts cab 6. Adaptive or predictive control algorithms canuse the parameters to predict movement of cab 6 caused by the forces.Fuzzy logic control algorithms may also be used to generate controlsignals in response to the force parameters to provide improved ridequality. Empirical testing may be used to determine the controlalgorithms.

Referring to FIG. 12, positioning control system 258 includes apositioning control circuit (PCC) 300 for receiving, processing andcommunicating site-specific data. PCC 300 is coupled to an interfacecircuit 302 for communicating across bus 208. PCC 300 also communicateswith external systems such as a computer 304 via a memory card 306 whichtransfers geo-referenced maps including spatially-variable map dataindicative of fields, roads and the bumpiness thereof. Card 306 can be aType II PCMCIA card made by Centennial Technologies, Inc. PCC 300includes a digital processor and memory. However, dedicated, specificpurpose equipment or hard-wired logic circuitry can also be used.

PCC 300 communicates with an operator through a user interface 308 via abus 310 (e.g., RS-232/485 interface). Interface 308 can include, forexample, a graphical user interface 312 providing cursor control (e.g.,a mouse, joystick or four-way switch), assignable switches 314 (e.g.,push buttons) configurable by PCC 300, a keyboard 316 and a voiceinterface 318. PCC 300 generates display signals applied to areconfigurable display 320 (e.g., CRT, flat screen active-matrix LCD)via a bus 322. Display 320 can display, inter alia, the configuration ofswitches 314. User interface 308 and display 320 are located in cab 14for easy operator access. PCC 300 may communicate with a printer 324 viaan interface 326 (e.g., an RS-232 link).

PCC 300 also communicates with a location signal generation circuit 328which generates location signals representing the positions of vehicle2. Circuit 328 includes a global positioning system (GPS) receiver 330with an associated antenna 332, and a differential GPS (DGPS) receiver334 with an associated antenna 336. A single antenna may be used inplace of antennas 332 and 336. GPS receiver 330 may be made by TrimbleNavigation Ltd. of California, and DGPS receiver 334 may be made bySatloc, Inc. of Arizona. GPS receiver 330 determines longitude andlatitude coordinates (and altitude) of the vehicle from signalstransmitted by the GPS satellite network. Accuracy of the position datais improved by applying correction signals received by DGPS receiver334. In one embodiment, PCC 300 interfaces with the SATLOC L-BandIntegrated TerraStar DGPS System via an RS-485 link.

PCC 300 receives signals representing the ground speed of vehicle 2 fromground speed sensor 338 via interface 340 (e.g., a frequency interface).Ground speed sensor 338 preferably includes a radar device mounted tothe body of vehicle 2. However, sensor 338 may also include a magneticpickup sensor configured to sense the speed of the vehicle's wheels ortransmission.

Referring to FIG. 13, bumpiness level data used to adjust theperformance parameters of ACS 26 may also be determined using vehicleposition as an index to geo-referenced maps of surface 12. For example,PCC 300 is provided with predetermined geo-referenced maps or datalayers 350 stored on memory card 306. Map 350 is represented by a tablewherein rows represent field locations and columns represent thelongitude and latitude coordinates, altitude and the bumpiness level foreach location. In one embodiment, bumpiness levels are represented usingdiscrete numbers (e.g., level 1=a relatively smooth surface, level 2=amedium surface, level 3=relatively bumpy surface). Other levels may alsobe defined and real numbers may be used. For example, data point no. 3indicates that the altitude is 801.0 feet and the surface is relativelysmooth at the location defined by latitude and longitudecoordinates--88.7290720 and 39.0710740, respectively. Map 350 ispreferably implemented using a geographical information systems (GIS)database stored as a DOS file on card 306.

Referring to FIG. 14, a predetermined geo-referenced map 350 of a road352 and a field 354 which includes bumpiness level data is representedgraphically. Road 352 is labeled bumpiness level 1 since it isrelatively smooth. One area of field 354 is labeled level 2 since it hasmedium bumpiness, while a second area 358 of field 354 (i.e., areawithin the polygon) is labeled as level 3 since it is relatively bumpy.The bumpiness level data stored in map 350 may have been generatingduring a previous pass of vehicle 2 by storing the signals that weregenerated by movement sensors 84 (using appropriate filtering).Alternatively, scouting data may have been entered into map 350 usingcomputer 304, or map 350 may distinguish only between smooth areas(e.g., paved roads) and bumpy areas (e.g., fields) in which casebumpiness level data is not needed if it is assumed that roads aresmooth and fields are bumpy.

When the vehicle and implement are at positions shown by markers 360 and362, the vehicle is on road 352 and the expected course of travel shownby arrows 364 indicates that the vehicle is expected to turn into field354. The current bumpiness level is level 1, and a bumpiness level of 2is expected after the turn. Similarly, when the vehicle and implementare located at positions shown by markers 366 and 368, the vehicle is inthe smoother area of field 354 (level 2) and is about to enter the bumpyarea (level 3). PCC 300 can use the current position of the vehicle andgeo-referenced map 350 to estimate the bumpiness level that the vehiclewill encounter and to adjust the performance parameters of ACS 26 toaccommodate changes in the level of bumpiness.

Referring to FIG. 15, vehicle 2 is equipped with another embodiment ofan active suspension system which includes an active vibration isolator400 mounted between a side 402 of cab 6 and a support member 404extending from chassis 4. Active or passive isolators or supports 406between cab 6 and chassis 4 allow the cab to move in response toactuations of isolator 400.

Isolator 400 may be the same as isolator 28. Since isolator 400 nolonger supports the static weight of cab 6, however, spring 44 may beeliminated or have a reduced weight capacity. Eliminating spring 44eliminates the need for a compressed air source, reduces power used bythe system, and reduces cost. To maximize response to cab pitch,isolator 400 is mounted high on side 402 of cab 6. Member 404 may be anengine compartment wall or another vertical support structure securelymounted to chassis 4. Alternatively, member 404 could be oriented alongthe longitudinal direction of vehicle 2 such that the system isresponsive to roll. Isolators 406 may be existing cab mounts. Multipleisolators 400 may be used on side 402 of cab 6 to provide-isolation inother axis' such as that provided by bottom-mounted isolators 28-32.Isolator 400 provides control in the longitudinal direction. However,active isolators can also be mounted so as to control movement of cab 6in the six degrees of freedom.

A particular application of an active suspension system for a workvehicle may use all or a subset of the sensors, actuators and otherfeatures and components disclosed above, and may include differentcombinations of the various alternatives. While the embodimentsillustrated in the FIGURES and described above are presently preferred,it should be understood that these embodiments are offered by way ofexample only. For example, depending upon the application, anair-operated actuator 68 may be used in place of a hydraulic actuator.Furthermore, an application may permit use of an electric (e.g.,solenoid-type) actuator. The power sources for these actuators includepressurized hydraulic fluid, pressurized air, and electricity,respectively. Also, active isolators may also be mounted to provideisolation for the six degrees of freedom of the cab. The invention isnot limited to any particular embodiment, but extends to variousmodifications that nevertheless fall within the scope of the appendedclaims.

What is claimed is:
 1. An active cab suspension system for a workvehicle, the work vehicle including a chassis, an operator's cabdisposed above the chassis, and another vehicle system having aparameter related to a force applied to the chassis which causesvibrations of the chassis which are transmitted to the cab, the activecab suspension system comprising:at least one active vibration isolatormounted at a location between the cab and the chassis and responsive toa control signal to control movement of the cab relative to the chassis;a communication interface coupled to the another vehicle system; andcontrol circuit coupled to the isolator and the communication interface,the control circuit configured to receive the parameter of the anothervehicle system from the communication interface, to generate the controlsignal at least partly in response to the parameter, and to apply thecontrol signal to the active vibration isolator to attenuatetransmission of vibrations from the chassis to the cab, the vibrationscaused by the force acting on the chassis, wherein frequency vibrationisolation is provided between the chassis and the cab.
 2. The active cabsuspension system of claim 1 further including a first sensor configuredto generate a first sensed signal indicative of movement of the cabcaused by disturbances in the chassis, wherein the control signalprimarily depends upon the first sensed signal and secondarily upon theparameter of the another vehicle system.
 3. The active cab suspensionsystem of claim 2 further including a second sensor configured togenerate a second sensed signal indicative of displacement between thecab and the chassis, wherein the control signal further depends upon thesecond sensed signal.
 4. The active cab suspension system of claim 2wherein the parameter of the another vehicle system causes a change insystem gain.
 5. The active cab suspension system of claim 1 wherein thework vehicle includes a tractor and the parameter is a draft forcesignal indicative of a draft force applied to the work vehicle by animplement.
 6. The active cab suspension system of claim 1 wherein theparameter is a clutch signal indicative of a clutch force applied to thework vehicle.
 7. The active cab suspension system of claim 1 wherein theparameter is a gear shift signal indicative of a gear shift forceapplied to the work vehicle.
 8. The active cab suspension system ofclaim 1 wherein the parameter is a brake signal indicative of a brakingforce applied to the work vehicle.
 9. The active cab suspension systemof claim 1 wherein the parameter is a speed actuator signal indicativeof an acceleration force applied to the vehicle.
 10. The active cabsuspension system of claim 1 further comprising an operator presencesensor coupled to the control circuit, wherein active movement of thecab is disabled when presence of the operator is not detected.
 11. Theactive cab suspension system of claim 1, wherein the frequency vibrationisolation provided between the chassis and the cab isolates thetransmission of low-frequency vibrations between the chassis and thecab.
 12. The active cab suspension system of claim 11, wherein thelow-frequency vibrations are below 20 Hz.
 13. The active cab suspensionsystem of claim 1, wherein the communication interface includes avehicle data bus.
 14. A work vehicle, comprising:a chassis; anoperator's cab disposed above the chassis; an active cab suspensionsystem including at least one active vibration isolator mounted betweenthe cab and the chassis and responsive to a control signal to controlmovement of the cab relative to the chassis; another vehicle systemhaving a parameter related to a force applied to the chassis whichcauses vibrations of the chassis which are transmitted to the cab; and acommunication interface coupled between the active cab suspension systemand the another vehicle system; wherein the active cab suspension systemfurther includes a control circuit coupled to the communicationinterface and configured to receive the parameter of the another vehiclesystem, to generate the control signal at least partly in response tothe parameter, and to apply the control signal to the active vibrationisolator to attenuate transmission of vibrations from the chassis to thecab, the vibrations caused by the force acting on the chassis, whereinfrequency vibration isolation is provided between the chassis and thecab.
 15. The work vehicle of claim 14 further including a first sensorconfigured to generate a first sensed signal indicative of movement ofthe cab caused by disturbances in the chassis, wherein the controlsignal depends primarily upon the first sensed signal and secondarilyupon the parameter of the another vehicle system.
 16. The work vehicleof claim 14 wherein the work vehicle is a tractor, the another vehiclesystem includes a height control system coupled to an implement, and theparameter is a draft force signal indicative of a draft force applied tothe work vehicle by the implement.
 17. The work vehicle of claim 14wherein the another vehicle system is selected from the group consistingof a steering control system, a clutch control system, a transmissioncontrol system, a brake control system and a speed control system, andthe parameter is indicative of a force applied to the vehicle by theselected another vehicle system.
 18. An active seat suspension systemfor a work vehicle, the work vehicle including a chassis, an operator'sseat supported by the chassis, and a second vehicle system having aparameter related to a force applied to the chassis which causesvibrations of the chassis which are transmitted to the seat, the activeseat suspension system comprising:at least one active vibration isolatormounted at a location between the seat and the chassis and responsive toa control signal to control movement of the seat relative to thechassis; a communication interface coupled to the second vehicle system;and a control circuit coupled to the communication interface and theactive vibration isolator, the control circuit configured to receive theparameter of the second vehicle system from the communication interface,and to generate the control signal applied to the vibration isolator atleast partly in response to the parameter, wherein transmission ofvibrations from the chassis to the seat is attenuated, the vibrationscaused by the force acting on the chassis, wherein frequency vibrationisolation is provided between the chassis and the seat.
 19. The activeseat suspension system of claim 18 further including a first sensorconfigured to generate a first sensed signal indicative of movement ofthe seat caused by disturbances in the chassis, the control signaldepending primarily upon the first sensed signal and secondarily uponthe parameter of the second vehicle system.
 20. The active seatsuspension system of claim 19 further including a second sensorconfigured to generate a second sensed signal indicative of displacementbetween the seat and the chassis, the control signal further dependingupon the second sensed signal.
 21. The active seat suspension system ofclaim 18 wherein the second vehicle system includes a clutch and theparameter is a clutch signal indicative of a clutch force applied to thevehicle, and movement of the seat due to the clutch force is attenuated.22. The active seat suspension system of claim 18 wherein the secondvehicle system includes a transmission and the parameter is a gear shiftsignal indicative of a gear shift force applied to the vehicle, andmovement of the seat due to the gear shift force is attenuated.
 23. Theactive seat suspension system of claim 18 wherein the second vehiclesystem includes a brake and the parameter is a brake signal indicativeof a braking force applied to the vehicle, and movement of the seat dueto the braking force is attenuated.
 24. The active seat suspensionsystem of claim 18 wherein the second vehicle system includes a speedactuator and the parameter is a speed actuator signal indicative of anacceleration force applied to the vehicle, and movement of the seat dueto the acceleration force is attenuated.
 25. An active cab suspensionsystem for a work vehicle, the work vehicle including a chassis, anoperator's cab disposed above the chassis, and a second vehicle systemhaving a parameter related to ground speed of the work vehicle, theactive cab suspension system comprising:at least one active vibrationisolator mounted at a location between the cab and the chassis andresponsive to a control signal to control movement of the cab relativeto the chassis; a communication interface coupled to the second vehiclesystem; and a control circuit coupled to the communication interface andthe active vibration isolator, the control circuit configured to receivethe parameter of the second vehicle system from the communicationinterface, to generate the control signal applied to the isolator toattenuate movement of the cab when the ground speed is above apredetermined speed threshold, and to disable cab movement when theground speed is below the threshold.
 26. An active cab suspension systemfor a work vehicle, the work vehicle including a chassis, an operator'scab disposed above the chassis, and another vehicle system having aparameter related to a force about to be applied to the work vehicle,the active cab suspension system comprising:at least one activevibration isolator mounted at a location between the cab and the chassisand responsive to a control signal to control movement of the cabrelative to the chassis; a communication interface coupled to theanother vehicle system; and a control circuit coupled to the isolatorand the communication interface, the control circuit configured toreceive the parameter of the another vehicle system from thecommunication interface, to predict the force about to be applied to thework vehicle based upon the parameter, to generate the control signal atleast partly in response to the predicted force, and to apply thecontrol signal to the active vibration isolator to attenuate movement ofthe cab due to the force about to be applied to the work vehicle,wherein the parameter is used as a preparatory signal.
 27. The activecab suspension system of claim 26, wherein the application of thecontrol signal to the active vibration isolator causes a bias in fluidsupply to the active vibration isolator.